Planetary gear system for speed changing of variable ratio transmissions

ABSTRACT

A SLIDABLE PULLEY SECTION OF A VARIABLE RATIO TRANSMISSION IS ADJUSTED ON ITS SHAFT TO CHANGE THE TRANSMISSION RATIO BY THE AID OF AN AUXILIARY REVERSIBLE PLANETARY GEAR DRIVE. THE AUXILIARY DRIVE CONNECTS THE SHAFT OF THE MAIN TRANSMISSION ITSELF TO THE SLIDABLE PULLEY SECTION. PARTS OPERABLE MANUALLY OR BY REMOTE CONTROL INITIATE OPERATION OF THE NORMALLY IDLE PLANETARY GEAR MECHANISM. THE VARIABLE RATIO TRANSMISSION MECHANISM MAINTAINS ITS ADJUSTMENT UNTIL THE AUXILIARY PLANETARY DRIVE IS OPERATED. THE AUXILIARY DRIVE IS MOUNTED SO THAT IT CAN BE REMOVED IN A UNIT IN A VERY SIMPLE MANNER, THUS TO FACILITATE BELT CHANGE OF THE MAIN VARIABLE RATIO TRANSMISSION MECHANISM. BY A UNIQUE ARRANGEMENT OF GUIDING TRACKS, NO SPIDER IS NECESSARY TO MAINTAIN THE PLANET GEARS IN POSITION.

Fixed upon the same shaft as pinion gear 115 and rotatable therewith is a gear 122 drivable by a gear 123 fixed upon the output shaft of an electrically energizable motor 124, the motor being physically supported from carriage support block 99 by bracket 125. Disposed flatwise on the floor of the box 88 is a. photographic film 126 suitable for variable exposure by the glow modulator 103. Signal current is provided to the glow modulator 103 through electrical cable 127 while control signals are sent to actuators 105, 106, 118 and 120 through cables 128, 129, 130 and 131 respectively, and the motor 124 is energized and deenergized through cable 132.

The apparatus of FIG. is utilized in conjunction with the circuitry arrangement illustrated in FIG. 9. From FIG. 9 it is observed that the glow modulator 103 receives signals through cable 127 from a lamp driver circuit 133 after the latter has processed the pre-recorded data signals routed to it over line 134 from the data channel 74 of the tape recorder 75 operating in its playback mode. The data signals read out of the tape data channel and into the lamp driver circuit 133 are variable amplitude signals as previously indicated, their power level being increased, expanded or compressed in accordance with the signal current requirements of the glow modulator 103 for purposes of producing a proper exposure of film 126. Operation of the lamp driver circuit 133 is controlled by exposure con trol .135 which may in a simple case be an amplifier bias control. The light output from glow modulator 103 is focused to the desired resolution in the film plane by a focusing device 136.

The recorded control signals are read out of control signal channel 81 of the tape unit 75 to an output line 137 connected to the signal input terminals of frequency selective resonant circuits 138, 139 and 140 which permit the passage therethrough of only that control signal of the indicated frequency. As shown, the resonant circuits 138, 139 and 140 permit the passage therethrough respectively of signal frequencies of 570 cycles, 210 cycles and 166 cycles. These resonant circuits may also include power amplifiers if required to drive the circuitry connected to the output terminals thereof.

The 166 cycle resonant circuit 140 will pass control signals only at the beginning and the end of the playback operation since these frequencies are only generated by the data collection apparatus when the start switch and stop switch are closed as indicated from FIG. 8. The output of circuit 140 drives a start/stop stepping switch 141 which has its contacts arranged so that alternate ones energize the drive motor 124 and intermediate ones deenergize the drive motor. Thus, the first pulse of 166 cycle energy steps switch 141 to energize the drive motor 124 at the beginning of the playback operation, and the final 166 cycle signal on the tape steps switch 141 to its next position to deenergize the drive motor 124 and terminate the read out scan. :3

The output pulses from the 570 cycle and 210 cycle resonant circuits 138 and 139 are utilized to actuate the left shift actuator 105 and right shift actuator 106 to produce carriage shift and move the glow modulator 103 to successive scanning lines, the outputs from these circuits also selectively actuating the upper and lower chain clamping actuators 118 and 120 to selectively clamp either the chain upper run or the chain lower run against the anvil and carrier block 102 to thereby cause the glow modulator 103 to traverse a scanning line while it is receiving data signal information for exposure of the underlying film 126. The upper and lower actuators 118 and 120 are not directly actuator by the resonant circuits 138 and 139' for two reasons.

First, it will be recalled that the pulses of signal energy recorded in the control signal channel from the tone generators 76 and 77 of FIG. 8 only exist during the time when the radiation detector apparatus undergoes its pause at the end of each scanning run. Consequently, the pulse energy if delivered to the actuators directly would only actuate them at precisely the times when it is desired to stop scanning motion of the glow modulator and would not actuate them during the scan time. Consequently, no scanning would occur. Secondly, it is desired that the glow modulator 103 stops scanning at the end of each scanning line during the time of carriage shift from the completed scan line to the next line about to be scanned. In this manner the movements of the glow modulator are synchronized with movements of the radiation detector of the data'collecting apparatus. In substance then, it is desired to selectively actuate the upper and lower chain clamping actuators 118 and 119 in the time interval between 210 cycle and 570 cycle control pulses, and to deactuate both of these actuators in the presence of either control pulse.

This is accomplished by employing a latching type relay designated in FIG. 9 as having two coils RIA and RIB both of which are coupled to the pole 142 for transferring the latter between contacts 143 and 144, and a relay R2 non-selectively energizable by control signals from either of the circuits 138 and .139 and effective when energized to break the circuit between normally closed pole 145 and contact 146. Contact 146 of relay R2 is connected to a source of positive potential while pole 142 of relay R1 is connected to a source of negative potential so that lower actuator 120- is energized whenever relay R2 is deenergized and when pole 142 is engaged with contact 143, all as illustrated in FIG. 9. Similarly, upper actuator 1.18 is energized when relay R2 is deenergized and pole 142 is engaged with contact 144. Thus, the selection of upper or lower actuator 118 or 120 is controlled by the latching relay R1, and energization of these actuators is controlled by the state of relay R2, both actuators being deenergized wlien R2 is energized to disengage pole 145 from contact 146 while the selected actuator is energized when relay R2 is deenergized.

With the foregoing in mind, operation of the apparatus of FIG. 5 by the prerecorded tape signals reading out of tape recording unit 75 is as follows. With the glow modulator 10-3 positioned at the drive motor end of its carriage, the tape unit is put into operation and the first recorded 166 cycle energy pulse passes through resonant circuit 140 to actuate stepping switch 141 and start the drive motor 124. The first 570 cycle control signal occurs next and energizes less shift actuator 105, relay R2 and coil RlA of latching relay R1. Energization of left shift actuator shifts the carriage one scanning line. Energization of coil RIA insures that pole 142 engages contact .143 to energize lower chain drive actuator as soon as the control pulse terminates and deenergizes relay R2. Lower actuator 120 clamps the lower chain run to carrier block 102 and initiates scanning of glow modulator 103 across the film and exposure of the latter by the data signals being delivered to the glow modulator.

Scanning continues until the 210 cycle energy pulse is received at the end of the first scanning line. This pulse energizes right shift actuator 106 to step the carriage to the next scanning line, energizes relay R2 to deenergize the chain clamping lower actuator 120, and energizes coil RIB of latching relay R1 to disengage pole 142 from contact 143 and engage the pole with contact 144 and thereby condition upper chain clamping actuator 118 for energization at the termination of the 210 cycle pulse when R2 will again be deenergized. At termination of this pulse the carrier block 102 is clamped to the upper chain run by actuator 118 and glow modulator begins its second scan in the reverse direction to the first scan.

This operation continues repetitively until all of the data has been read out and the 166 cycle stop signal appears on the control signal output line 137, passes through resonant circuit and steps switch .141 to its next position thereby deenergizing drive motor 124 and terminating the read out operation. The film 126 may then be photographically processed to obtain a finished print of the data. Should an underexposure or overexposure of the film have occurred, a new run may be immediately made Sept. 21, 1971 w, R, TMLER 3,606,799

SYST OF PLANETARY GEAR FOR SPEED CH ING VARIABLE RATIO TRANSMISSION Filed Feb. 4, 1970 2 Sheets-Sheet 2 Lara. 3.

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United States Patent O US. Cl. 74230.17 7 Claims ABSTRACT OF THE DISCLOSURE A slidable pulley section of a variable ratio transmission is adjusted on its shaft to change the transmission ratio by the aid of an auxiliary reversible planetary gear drive. The auxiliary drive connects the shaft of the main. transmission itself to the slidable pulley section. Parts operable manually or by remote control initiate operation of the normally idle planetary gear mechanism. The variable ratio transmission mechanism maintains its adjustment until the auxiliary planetary drive is operated. The auxiliary drive is mounted so that it can be removed in a unit in a very simple manner, thus to facilitate belt change of the main variable ratio transmission mechanism. By

a unique arrangement of guiding tracks, no spider is necessary to maintain the planet gears in position.

RELATED APPLICATION This application is a continuation-in-part of my copending application Ser. No. 730,798 filed May 21, 1968, new US. Pat. No. 3,516,296 entitled Adjustment Mechanism for Variable Ratio Transmission.

BACKGROUND OF THE INVENTION (a) Field of the invention This invention relates to variable ratio transmissions, particularly the type utilizing variable diameter pulley structures such as shown in United States Letters Patent No. 3,250,141. In such mechanisms, an input shaft carries a pair of opposed conical pulley sections, one being fixed on the shaft and the other being slidable on the shaft whereby the effective pulley diameter is changed in a well understood manner. In my prior application Ser. No. 730,798 filed May 21, 1968, entitled Adjustment Mechanism for Variable Ratio Transmission, a variety of auxiliary drive mechanisms are shown and described that adjust the main variable ratio transmission by using power from the main shaft itself.

(b) Objects of the invention The primary object of this invention is to provide improved auxiliary drive mechanisms of the type shown and described in my said prior application. In particular, one of the objects of this invention is to provide a selfcontained unit that, upon removal of a single screw, can be detached as a unit with the movable pulley section of the main transmission mechanism whereby worn belts may be replaced with a minimum of difiiculty.

Another object of this invention is to provide an auxiliary drive mechanism of this character that provides the requisite gear reduced operation but is comprised of a minimum number of parts. Unique tracks make it possible to eliminate spiders otherwise required to hold the planetary gears in equiangularly spaced parallel relationship.

Still another object of this invention is to provide a compact auxiliary drive of this character the operative gear parts of which are neatly enclosed.

3,606,799 Patented Sept. 21, 1971 BRIEF DESCRIPTION OF THE DRAWINGS A detailed description of the invention will be made with reference to the accompanying drawings. These drawings, unless described as diagrammatic or unless otherwise indicated, are to scale.

FIG. 1 is a fragmentary axial sectional view of a variable ratio transmission mechanism incorporating the present invention.

FIGS. 2 and 3 are sectional views taken along planes corresponding to lines 2-2 and 3-3 of FIG. 1.

DETAILED DESCRIPTION The following detailed description is of the best presently contemplated mode of carrying out the invention. This description is not to be taken in a limiting sense, but is made merely for the purpose of illustrating the general principles of the invention since the scope of the invention is best defined by the appended claims.

The variable ratio transmission mechanism includes an input shaft and an output shaft supported in spaced parallel relationship. These shafts, in a well understood manner, carry variable diameter pulley structures connected by the aid of a belt. FIG. 1 shows a portion of such apparatus, namely, the belt 8, the input shaft 10 and the movable half of the variable diameter pulley structure carried by the shaft 10. The pulley section 12 has a hub 14 mounted for sliding" movement on the shaft. Plastic collars 16 and 18 line the bore of the hub and serve to reduce friction. A key 20 serves to couple the pulley section 12 to the shaft 10 and is accommodated in opposed keyways formed in the hub bore and on the exterior of the shaft 10. The key moves axially with the pulley section 12. For this purpose the key has a projection 22 entering a corresponding recess in the hub 14. In a manner to be hereinafter described, the pulley section can be moved off the shaft in order to change a worn belt.

The pulley section 12 is moved axially and held in axially adjusted position by the aid of an auxiliary drive mechanism. This auxiliary drive mechanism includes a cup-like input member 24 attached to the end of the drive shaft 10 and rotatably coupled to it. The auxiliary drive also includes a sleeve-like output member 26. The output member 26 has an interiorly threaded sleeve part 28 that engages exterior threads on the hub 14. The axial position of the output member is fixed by interfitting flanges 29 and 30 of the input and output members. When the output drive member 26 is rotated relative to the input member 24 and the shaft 10, the pulley section 12 is thus caused to move axially in one direction or the other in accordance with the direction of relative rotation.

The input member 24 has a recess 31 fitted on the end of the shaft 10. A projection 32 enters the shaft keyway so that the input member rotates with the shaft. An attaching bolt 34 extends through an aperture of the drive input member 24 and engages a tapped bore 35 in the end of the shaft 10 to hold the input member in place.

Planetary gearing connects the input and output members 24 and 26. The input member carries a gear 36 located close to the outer end of the output drive memher. The output drive member 26 has thereon a similar gear 38 located at its outer end. Both gears 36 and 38 are on the same pitch circle, but have a slightly different number of teeth. Three planetary gear units 40 (see also FIGS. 2 and 3) are located in relationship about the input and output member gears 36 and 38. Each gear unit 40 has two gear sections located in end-to-end relationship. One of the gear sections 42 is elongated and meshes simultaneously with the input and output gear members 3 36 and 38. Upon corresponding rotation of the planetary gears about their axes, the output drive member 26 is rotated relative to the input drive member 24.

The left-hand or inner end 43 of each gear unit 40 is cylindrical, the gear teeth of section 42 terminating short of the end. This end 43 rides along a circular track 4 4 formed at the base of the radially extending flange 46 of the output drive member 26. The other or outer end of each gear unit 40* has a spur gear section 48 of larger pitch diameter that extends with clearance along the side of the input member gear 36. The function of this section 48 will be hereinafter described.

In order to impart planetary movement to the gear units 40 in one direction, thus to shift the pulley section correspondingly, a floating ring gear control member 50 is provided. This ring gear 50 continually meshes with the outer elements of all of the planetary gear sec tions 42. The ring gear is located concentrically by the aid of a circular track 51 that cooperates with the cylindrical ends 43 of the gear units 40'. The flange 46 limits axial movement in one direction. The axes of the planetary gear units are accurately located at the region of the inner ends 43 by virtue of the coaxial circular surfaces 44 and 51 of the output member 26 and the ring gear 50.

The axes of the planetary gear units 40 at the region of the outer ends are also accurately located. Thus the ring gear 50 extends axially and terminates just short of the side of the spur gear section 48. A cylindrical hub part 52 at the base of each gear section 48 at the outer end of the section 42 fits into a cylindrical end 54' 0f the ring gear. The hub part 52 also fits a cylindrical register 55 at the outer end of the input gear member 36. All of the gear units 40 are thus accurately stabilized even though no spider is provided. The axes of the planetary gear units are confined to a common circular orbit of substantially fixed radius, and the degree of mesh of the gears is controlled. Each of the planetary gear units 40 can, of course, be made as a composite unit.

The ring gear 50 normally rotates with the planetary gear units whereby no relati've planetary motion results. However, if the floating ring gear 50 is retarded relative to the shaft 10, planetary motion in one direction results. For this purpose, a friction brake is provided.

The brake includes a plunger 56 movable to engage a cylindrical surface 57 formed on the periphery of the floating ring gear 50. The plunger 56 is guided for radial movement by the casing 58 or a part attached to the casing. A spring 60 normally retracts the plunger 56. The plunger may carry a head lined with suitable friction material. The plunger may be moved manually or by a remotely controlled solenoid coil (not shown).

In order to cause planetary motion in the opposite direction, a sun gear control member 64 is provided. The sun gear control member is rotatably supported on the outer end of the input drive member 24. The control member has a radial flange 66 that cooperates with the flange 46 to limit axial movement. At the base of the flange 66 is a sun gear 68 that continually meshes with the inner elements of all of the spur gear sections 48 of the planetary gear units.

The sun gear control member 64 normally rotates with the shaft 10 and the input drive member 24. However, if the sun gear is retarded, planetary motion is imparted to the assembly 40 in the opposite direction from that resulting when the ring gear 50 is retarded. In order to retard the floating sun gear control member 64-, it is provided with an annular brake surface 70 formed on a cylindrical rim flange 72. A plunger 76 operates a brake similar to the brake for the ring gear 50.

The spur gear sections 48 are designed to provide the same planetary movement in the reverse direction that the ring gear 50 causes in the forward direction for the same slip. A substantial gear reduction is accomplished in both directions in order to achieve a sensitive adjustment of the slidable pulley section.

The cylindrical rim flange 72 overlies the spur gear sections 48 as well as part of the ring gear 50. The planetary gear structure is thus enclosed. A flange 82 reduces the clearance between the parts.

In order to provide access to the belt 8, it is merely necessary to remove the attaching bolt 34 which may have a wrench socket (not shown). When so removed, the entire auxiliary drive together with the pulley section 12 is removable as a unit. The pulley section 12 and the input drive member 24 together slide off the shaft.

The pulley section 12 carries an indicator 88 of the type shown and described in my prior application Serial No. 730,798. This indicator cooperates with a dial or scale at an aperture in the case (not shown) thus to indicate the approximate ratio of the variable ratio transmission mechanism.

I claim:

1. In a variable ratio transmission having a shaft and a pulley section slidable along the end of the shaft, said pulley section being keyed or otherwise coupled to the shaft for rotation therewith: an auxiliary drive for shifting said pulley section and determining the axial position thereof, said auxiliary drive including (a) an input drive member deta'chably secured to the end of the shaft;

(b) means keying or otherwise coupling the input drive member to the shaft for rotation therewith;

(c) an output drive member rotatably supported on said input drive member at an axial position that is substantially fixed;

(d) a threaded coupling between said output drive member and said pulley section operative to move said pulley section axially upon relative axial movement between said output drive member and said pulley section; said threaded coupling serving to connect said output drive member and said pulley section for removal from said shaft together with said input drive member;

(e) normally inactive reversible transmission elements between and carried by said input drive member and said output drive member; and

(f) selectively operable means for rendering said transmission elements operative in a selected direction.

2. The combination as set forth in claim 1 in which said reversible transmission elements form with said input and output members a differential transmission having alternately operable auxiliary control members; and means selectively retarding one of said auxiliary control members in order to cause rotation of said output member in one direction or the other.

3. The combination as set forth in claim 2 in which said reversible transmission elements are a plurality of similarly but angularly spaced planetary gear units, said input member and said output member having side-byside gears on the same pitch but with slightly different numbers of teeth simultaneously in mesh with said planetary gear units; said auxiliary control members comprising a first ring gear control member engaging said planetary gear units, and a second sun gear control member engaging said planetary gear units axially beyond said side-by-side gears of said input and output drive members.

4. The combination as set forth in claim 3 in which said output drive member has a radial flange on one side of said side-by-side gears; said auxiliary control members together with said flange enclosing said side-by-side gears, said planetary gear units, said ring gear and said sun gear, said auxiliary control members having peripheral annular bands cooperable with braking members selectively cooperable therewith.

5. In a variable ratio transmission having a shaft provided with a keyway, said transmission also including a pulley section having an externally threaded hub slidable along the end of the shaft, said pulley section being keyed to the shaft for rotation therewith: an auxiliary drive for shifting said pulley section and determining the axial position thereof, said auxiliary drive including:

(a) an input drive member having a recess fitted on the end of said shaft; said input drive member having a through axial bore;

(b) a screw extending through said bore and engaging a threaded aperture in the end of said shaft for attaching said input drive member thereto;

(c) key means carried by the input drive member cooperable with said shaft keyway;

(d) an output drive member rotatably mounted on said input drive member at a substantially fixed axial position, said output drive member having at its inner end an internally threaded sleeve threadedly engaging the hub of said slidable pulley section, said output drive member having an intermediate radial flange;

(c) said input and output drive members having side-by-side gears on the same pitch circle but having a different number of teeth, the gear on said output drive member being located at the base of said flange on the outer end of said output drive member;

(f) said flange having an intermediate step forming a circular track;

(g) three or more planetary gear units each having a first gear part in mesh with both of said side-bysido gears and located in equiangularly spaced rela tionship about the shaft axis;

(h) each of said planetary gear units having a cylindrical part atone end, the inner element of which engages said circular track of said flange;

(i) each of said planetary gear units having an enlarged second pinion part located outwardly beyond the gear of said input drive member;

(j) a ring gear control member having internal gear teeth simultaneously engageable with the first gear parts of said planetary gear units;

(k) said ring gear control member having at its inner end, an interior cylindrical surface engageable simultaneously with the outer elements of said cylindrical parts of said planetary gear units;

(1) said ring gear control member having at its outer end an interior cylindrical surface;

(In) said planetary gear units each having a cylindrical part adjacent the juncture of the first gear and second pinion parts thereof, the outer elements of which are in engagement with the cylindrical surface at the outer end of said ring gear control member;

(11) a sun gear control member rotatably mounted on said input drive member at a substantially fixed axial position and having a radial flange, the radial flanges of said output drive member and said sun gear control member together limiting axial movement of said planetary gear units;

(0) said sun gear control member having a gear at the base of its flange in engagement With the pinion part of said planetary gear units;

(p) said sun gear control member having a cylindrical outer flange having its distal end in partial encompassing relationship with said ring gear control member;

(q) the peripherally exposed portions of said ring gear control member and the cylindrical flange of said sun gear control members having annular brake surfaces;

(r) a pair of brake members individually guided for movement toward and away from said annular brake surfaces of said ring gear for selective retardation of one of the control members for causing planetary movement of said planetary gear units in one direction or the other thus to cause axial movement of the movable pulley section; and

(s) means forming a cylindrical track on said input drive member adjacent its said gear and engaging the inner elements of the cylindrical parts of said planetary gear units.

6. The combination as set forth in claim 5 in which the planetary gear parts have numbers of teeth relative to said ring gear and said sun gear such as to cause substantially equal planetary movement in opposite directions for the same percentage slip of said control members.

7. The combination as set forth in claim 6 together with remote control means for operating said brake members.

References Cited UNlTED STATES PATENTS 2,889,716 6/1959 Doty 74230.l7 3,250,141 5/1966 Luenberger 74-230.17 3,516,296 6/1970 Detwiler 74230.17

CORNELIUS I. HUSAR, Primary Examiner 

